Pressurized air induction system

ABSTRACT

Methods are provided for engines. In one example method, at higher engine load, cool compressed air is drawn into an engine via an air intake passage, and at lower engine load, ambient air is drawn into the engine via a duct while retaining cooled compressed air in the air intake passage. The compressed air may be released from the air intake passage based on heat transferred to the compressed air during the lower engine load, in at least one example.

CROSS REFERENCE TO RELATED APPLICATION

The present application is a divisional of U.S. Non-Provisional patentapplication Ser. No. 16/803,357, entitled “PRESSURIZED AIR INDUCTIONSYSTEM,” and filed on Feb. 27, 2020, which is a divisional ofapplication Ser. No. 15/826,401, entitled “PRESSURIZED AIR INDUCTIONSYSTEM,” and filed on Nov. 29, 2017. The entire contents of theabove-referenced applications are hereby incorporated by reference forall purposes.

FIELD

The present description relates generally to methods and systems forcontrolling a vehicle engine to provide a boosted air charge.

BACKGROUND/SUMMARY

By incorporating a turbocharger, comprising a compressor driven by aturbine, into an engine of a vehicle, the efficiency and power output ofthe engine may be improved. The forced induction of extra air into acombustion chamber of the engine proportionally induces the combustionof additional fuel, producing more power than obtained from air intakeat ambient pressure. The pressurized, or boosted, air is typicallyheated during compression and if combusted directly, may increase therisk of engine knock. Thus, boosted air is typically cooled by flowingthe air through a charge air cooler (CAC) before entering the engineintake manifold, a process that also increases the density of the airand improves intake throttle response.

The air compression provided by the compressor of the turbocharger isenabled by the rotation of the turbine. Typically, at least a portion ofthe exhaust gas is routed to the turbine and the expansion of theexhaust gas causes the turbine to spin. Since the turbine ismechanically coupled to the compressor, as the turbine spins up, so doesthe compressor. However, there may be a delay between the time when anincrease in torque is demanded and when the corresponding boost pressureis provided by the compressor. The delay, also referred to as turbo lag,is due to the turbine's inertia and friction when operating at lowengine loads, and corresponds to a duration required for the engine togenerate sufficient exhaust gas (e.g., exhaust flow and temperature) tospool up the turbine to drive the compressor. During this turbo lag,boosted engine performance may be degraded.

Various approaches have been developed to address the issue of turbo lagincluding providing an alternative pathway for supplying air to theengine. One example approach is shown by Sealy et al. in U.S. Pat. No.6,561,169. Therein, a charge air management system is disclosed whereina first air duct supplies air at ambient pressure to an intake manifoldand a second air duct flows cool, boosted air, from downstream of acharge air cooler (CAC), to the intake manifold. Air flow through thefirst air duct or the second air duct is controlled via a valve based onthe engine's speed and load. During low loads, air is delivered via thefirst duct. During higher loads, cooled, dense air is delivered via thesecond duct and the CAC.

However, the inventors herein have recognized potential issues with suchsystems. There may be conditions where the air provided via the secondduct does not improve boosted engine performance. In the approach ofSealy, closing of the valve during a low load condition allows cool anddense compressed air to be held within the second duct, and releasedwhen the valve is opened during a subsequent high load condition. Sincethe charge air management system of Sealy is adapted for infrequentdemands on the turbocharger, the CAC is not operated during low loadconditions to improve fuel economy. Consequently, based on ambientconditions, as well as a duration over which the compressed air is heldin the second duct without operation of the CAC, the boosting potentialof the compressed air may degrade. For example, during conditions whenthe ambient temperature or humidity is high, the density of thecompressed air held in the second duct may decrease, reducing theengine's throttle response when the compressed air is subsequentlyreleased. If the CAC is operated while air is retained in the sealedsecond duct, the fuel economy benefit of the boosted engine may be lost.

In one example, the issues described above may be addressed by a methodfor reducing turbo lag comprising; at higher engine load, drawing coolcompressed air into an engine via an air intake passage and at lowerengine load, drawing ambient air into the engine via a duct whileretaining cooled compressed air in the air intake passage. Additionally,compressed air is released from the air intake passage based on heattransferred to the compressed air during the lower engine load. In thisway, boost pressure response time following a transient increase intorque demand can be improved.

As one example, a dual pathway air induction system may be adapted to anengine of a vehicle. The induction system may include a first airpassage coupled to an intake manifold via a first throttle, the firstair passage configured to deliver fresh air at ambient pressure toengine cylinders at low engine speed and loads. The induction system mayfurther include a second air passage coupled to the intake manifold viaa second throttle, the second passage including a turbochargercompressor and a CAC for delivering cool, compressed air to the enginecylinders during high engine speeds and loads. The first passage may becoupled to the second passage via a coupling, such as a T-body.Additionally, flow to each passage may be controlled via a splittervalve (e.g., a proportional valve) or via respective first and secondthrottle valves. Responsive to an operator tip-in, flow through thesecond passage may be increased while flow through the first passage isdecreased. Responsive to a subsequent operator tip-out, CAC operation isdisabled, flow through the first passage may be increased, and flowthrough the second passage is closed to trap an amount of cool,compressed air within the second passage. A rate of temperature rise ofthe trapped air is estimated while the second passage is closed. Forexample, heat transfer to the trapped air may be estimated as a functionof ambient temperature, humidity, volume of air trapped, boost levelattained before the second throttle was closed, etc. If the amount ofheat transfer exceeds a threshold, such as when the inferred temperatureof the trapped air exceeds a threshold temperature, the enginecontroller may open the second throttle and release the trapped warmair, even if a higher torque was not demanded. The first throttle may becorrespondingly closed and one or more engine operating parameters maybe adjusted (e.g., spark timing may be retarded from MBT) to reducetorque transients.

In this way, by trapping cool, compressed air within a duct, the ductcan be used as a boost pressure reservoir that rapidly provides boostpressure to engine cylinders during a tip-in. As such, this reducesturbo lag. The technical effect of discharging the trapped compressedair while torque demand is low responsive to a rise in the inferredtemperature of the trapped air is that boost performance of the enginecan be maintained elevated. Specifically, only compressed air that iscool and dense, and therefore capable of improving throttle responsewhen discharged, is trapped inside the duct. By discharging trapped airthat is warm and less dense during conditions when boost demand is low,the adverse effect of the warm air on throttle response is reduced. Theduct can be replenished with fresh air that is rapidly cooled duringsubsequent CAC operation. In this way, boosted engine performance isimproved.

It should be understood that the summary above is provided to introducein simplified form a selection of concepts that are further described inthe detailed description. It is not meant to identify key or essentialfeatures of the claimed subject matter, the scope of which is defineduniquely by the claims that follow the detailed description.Furthermore, the claimed subject matter is not limited toimplementations that solve any disadvantages noted above or in any partof this disclosure.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 shows an example engine system for a single turbo boosted hybridvehicle.

FIG. 2 shows a schematic illustration of an engine adapted with apressurized air induction system.

FIG. 3A shows a top view of a first embodiment of the pressurized airinduction system.

FIG. 3B shows an isometric perspective view of the first embodiment ofthe pressurized air induction system.

FIG. 4A shows a top view of a second embodiment of the pressurized airinduction system.

FIG. 4B shows a cross-sectional view of the second embodiment of thepressurized air induction system.

FIG. 5 depicts a high level flow chart of an example method forcontrolling the operation of a pressurized air induction system.

FIGS. 6-7 show example operations of the pressurized air inductionreservoir system to improve boosted engine performance, according to thepresent disclosure.

FIGS. 3A-4B show example configurations with relative positioning of thevarious components. If shown directly contacting each other, or directlycoupled, then such elements may be referred to as directly contacting ordirectly coupled, respectively, at least in one example. Similarly,elements shown contiguous or adjacent to one another may be contiguousor adjacent to each other, respectively, at least in one example. As anexample, components laying in face-sharing contact with each other maybe referred to as in face-sharing contact. As another example, elementspositioned apart from each other with only a space there-between and noother components may be referred to as such, in at least one example. Asyet another example, elements shown above/below one another, at oppositesides to one another, or to the left/right of one another may bereferred to as such, relative to one another. Further, as shown in thefigures, a topmost element or point of element may be referred to as a“top” of the component and a bottommost element or point of the elementmay be referred to as a “bottom” of the component, in at least oneexample. As used herein, top/bottom, upper/lower, above/below, may berelative to a vertical axis of the figures and used to describepositioning of elements of the figures relative to one another. As such,elements shown above other elements are positioned vertically above theother elements, in one example. As yet another example, shapes of theelements depicted within the figures may be referred to as having thoseshapes (e.g., such as being circular, straight, planar, curved, rounded,chamfered, angled, or the like). Further, elements shown intersectingone another may be referred to as intersecting elements or intersectingone another, in at least one example. Further still, an element shownwithin another element or shown outside of another element may bereferred as such, in one example.

DETAILED DESCRIPTION

The following description relates to systems and methods for providingcold, boosted air to an engine system, such as the system of FIG. 1 ,via a pressurized air induction system, such as the system of FIG. 2 .The pressurized air induction system may include a first and a secondair pathway for air flow, each pathway coupled at a first end to a freshair duct and coupled at a second end to an intake plenum upstream of anengine cylinder. As shown in FIG. 2 , the first air pathway may flowfresh ambient air to the engine while the second air pathway may flowair via a compressor and a charge air cooler (CAC). Flow through thefirst and second pathways may be controlled via individual throttlevalves, as shown in the embodiment of FIGS. 3A-3B. Alternatively, therelative flow between the passages may be controlled via a splittervalve, as shown in the embodiment of FIGS. 4A-4B. A controller may beconfigured to perform a control routine, such as the example routine ofFIG. 5 , to adjust a position of the valve(s) based on engine speed-loadconditions so that an amount of cool, compressed air can be stored inthe second passage acting as a reservoir, the compressed air releasedresponsive to an increase in torque demand to reduce turbo lag. Thecontroller may also adjust the valve(s) to discharge any trapped airbased on an inferred amount of heat transferred into the air. Exampleoperations of the pressurized air induction system are illustratedherein with reference to FIGS. 6-7 . In this way, boosted engineperformance is improved.

FIG. 1 depicts an example of a cylinder of internal combustion engine 10of a vehicle 5. Engine 10 may be controlled at least partially by acontrol system including controller 12 and by input from a vehicleoperator 130 via an input device 132. In this example, input device 132includes an accelerator pedal and a pedal position sensor 134 forgenerating a proportional pedal position signal PP. Cylinder 14 (whichmay be referred to herein as a combustion chamber) of engine 10 mayinclude combustion chamber walls 136 with piston 138 positioned therein.Piston 138 may be coupled to crankshaft 140 so that reciprocating motionof the piston is translated into rotational motion of the crankshaft.Crankshaft 140 may be coupled to at least one drive wheel of thepassenger vehicle via a transmission system. Further, a starter motor(not shown) may be coupled to crankshaft 140 via a flywheel to enable astarting operation of engine 10.

Engine 10 is a boosted engine comprising a turbocharger 175 forproviding a boosted intake air charge. Although engine 10 is showncoupled to one turbocharger, other embodiments of engine 10 may includemore than one turbocharger to provide boost. Turbocharger 175 isconfigured with a compressor 174 and an exhaust turbine 176. Thecompressor 174 is arranged in an air intake passage 142, which drawsfresh ambient air into the engine 10. The compressor 174 is driven bythe exhaust turbine 176. Since the compression of air heats the aircharge, the boosted air is flowed through a charge air cooler (CAC) 192where it is cooled before being delivered to engine cylinders. CAC 192may be a water-air or air-air based heat exchanger. The turbine 176 ispositioned in an exhaust passage 148 downstream of the cylinder 14 andupstream of an emission control device 178. Turbine 176 is connected tocompressor 174 mechanically by a shaft 180. The rotation of turbine 176is driven by hot expanding exhaust gas flowing from cylinder 14 throughexhaust passage 148 towards emission control device 178, the spinning ofturbine 176 at least partially powering the rotation of the compressorvia the shaft 180. Engine 10 further includes a pressurized airinduction (PAI) system 199 configured to deliver air to cylinder 14. ThePAI system 199 includes a bypass duct 194 coupled at a first end to airintake passage 142 at a location upstream of compressor 174 and at asecond end to an intake plenum 146. In this way, bypass duct 194 mayconstitute a first air pathway of the PAI system 199 while air intakepassage 142 leading into air intake passage 198 including compressor 174and CAC 192 constitutes a second air pathway of the PAI system 199. Theconfiguration of the PAI system 199 is elaborated in detail at FIG. 2 .Example embodiments of the PAI system 199 are detailed at FIGS. 3A-3Band FIGS. 4A-4B.

Cylinder 14 can receive intake air via air intake passages 142, 198,144, and bypass duct 194 and the intake plenum 146, of which a generalrepresentation is shown in FIG. 1 . Intake plenum 146 can communicatewith other cylinders of engine 10 in addition to cylinder 14. FIG. 1shows engine 10 configured with the turbocharger 175 includingcompressor 174 arranged between intake passages 142 and 198 and turbine176 arranged along exhaust passage 148. Air intake passage 142 andbypass duct 194 flow air at ambient conditions while air intake passages198 and 144 contain air that is boosted briefly by compressor 174. TheCAC 192 may be disposed downstream of compressor 174 and upstream of afirst throttle 162 in air intake passage 198 with a pressure reliefvalve (PRV) 164 positioned in between compressor 174 and CAC 192. Thefirst throttle 162, which is also an air throttle, and a second throttle196, which is also a boost throttle, may be provided along bypass duct194 and intake passages 144, respectively, of the engine for varying theflow rate and/or pressure of intake air provided to the enginecylinders. For example, first throttle 162 may be positioned downstreamof a CAC 192 as shown in FIG. 1 , or alternatively may be providedupstream of CAC 192.

Exhaust passage 148 can receive exhaust gases from other cylinders ofengine 10 in addition to cylinder 14. Exhaust gas sensor 128 is showncoupled to exhaust passage 148 upstream of emission control device 178.Sensor 128 may be selected from among various suitable sensors forproviding an indication of exhaust gas air/fuel ratio such as a linearoxygen sensor or UEGO (universal or wide-range exhaust gas oxygen), atwo-state oxygen sensor or EGO (as depicted), a HEGO (heated EGO), aNOx, HC, or CO sensor, for example. Emission control device 178 may be athree way catalyst (TWC), NOx trap, various other emission controldevices, or combinations thereof.

Each cylinder of engine 10 may include one or more intake valves and oneor more exhaust valves. For example, cylinder 14 is shown including atleast one intake poppet valve 150 and at least one exhaust poppet valve156 located at an upper region of cylinder 14. In some examples, eachcylinder of engine 10, including cylinder 14, may include at least twointake poppet valves and at least two exhaust poppet valves located atan upper region of the cylinder.

Intake valve 150 may be controlled by controller 12 via actuator 152.Similarly, exhaust valve 156 may be controlled by controller 12 viaactuator 154. During some conditions, controller 12 may vary the signalsprovided to actuators 152 and 154 to control the opening and closing ofthe respective intake and exhaust valves. The position of intake valve150 and exhaust valve 156 may be determined by respective valve positionsensors (not shown). The valve actuators may be of the electric valveactuation type or cam actuation type, or a combination thereof. Theintake and exhaust valve timing may be controlled concurrently or any ofa possibility of variable intake cam timing, variable exhaust camtiming, dual independent variable cam timing or fixed cam timing may beused. Each cam actuation system may include one or more cams and mayutilize one or more of cam profile switching (CPS), variable cam timing(VCT), variable valve timing (VVT) and/or variable valve lift (VVL)systems that may be operated by controller 12 to vary valve operation.For example, cylinder 14 may alternatively include an intake valvecontrolled via electric valve actuation and an exhaust valve controlledvia cam actuation including CPS and/or VCT. In other examples, theintake and exhaust valves may be controlled by a common valve actuatoror actuation system, or a variable valve timing actuator or actuationsystem.

Cylinder 14 can have a compression ratio, which is the ratio of volumeswhen piston 138 is at bottom center to top center. In one example, thecompression ratio is in the range of 9:1 to 10:1. However, in someexamples where different fuels are used, the compression ratio may beincreased. This may happen, for example, when higher octane fuels orfuels with higher latent enthalpy of vaporization are used. Thecompression ratio may also be increased if direct injection is used dueto its effect on engine knock.

In some examples, each cylinder of engine 10 may include a spark plug193 for initiating combustion. Ignition system 190 can provide anignition spark to cylinder 14 via spark plug 193 in response to sparkadvance signal SA from controller 12, under select operating modes.However, in some embodiments, spark plug 193 may be omitted, such aswhere engine 10 may initiate combustion by auto-ignition or by injectionof fuel as may be the case with some diesel engines.

In some examples, each cylinder of engine 10 may be configured with oneor more fuel injectors for providing fuel thereto. As a non-limitingexample, cylinder 14 is shown including two fuel injectors 166 and 170.Fuel injectors 166 and 170 may be configured to deliver fuel receivedfrom fuel system 8. Fuel system 8 may include one or more fuel tanks,fuel pumps, and fuel rails. Fuel injector 166 is shown coupled directlyto cylinder 14 for injecting fuel directly therein in proportion to thepulse width of signal FPW-1 received from controller 12 via electronicdriver 168. In this manner, fuel injector 166 provides what is known asdirect injection (hereafter referred to as “DI”) of fuel into combustioncylinder 14. While FIG. 1 shows injector 166 positioned to one side ofcylinder 14, it may alternatively be located overhead of the piston,such as near the position of spark plug 193. Such a position may improvemixing and combustion when operating the engine with an alcohol-basedfuel due to the lower volatility of some alcohol-based fuels.Alternatively, the injector may be located overhead and near the intakevalve to improve mixing. Fuel may be delivered to fuel injector 166 froma fuel tank of fuel system 8 via a high pressure fuel pump, and a fuelrail. Further, the fuel tank may have a pressure transducer providing asignal to controller 12.

Fuel injector 170 is shown arranged in intake plenum 146, rather than incylinder 14, in a configuration that provides what is known as port fuelinjection (hereafter referred to as “PFI”) into the intake port upstreamof cylinder 14. Fuel injector 170 may inject fuel, received from fuelsystem 8, in proportion to the pulse width of signal FPW-2 received fromcontroller 12 via electronic driver 171. Note that a single driver 168or 171 may be used for both fuel injection systems, or multiple drivers,for example driver 168 for fuel injector 166 and driver 171 for fuelinjector 170, may be used, as depicted.

In an alternate example, each of fuel injectors 166 and 170 may beconfigured as direct fuel injectors for injecting fuel directly intocylinder 14. In still another example, each of fuel injectors 166 and170 may be configured as port fuel injectors for injecting fuel upstreamof intake valve 150. In yet other examples, cylinder 14 may include onlya single fuel injector that is configured to receive different fuelsfrom the fuel systems in varying relative amounts as a fuel mixture, andis further configured to inject this fuel mixture either directly intothe cylinder as a direct fuel injector or upstream of the intake valvesas a port fuel injector.

Fuel may be delivered by both injectors to the cylinder during a singlecycle of the cylinder. For example, each injector may deliver a portionof a total fuel injection that is combusted in cylinder 14. Further, thedistribution and/or relative amount of fuel delivered from each injectormay vary with operating conditions, such as engine load, knock, andexhaust temperature, such as described herein below. The port injectedfuel may be delivered during an open intake valve event, closed intakevalve event (e.g., substantially before the intake stroke), as well asduring both open and closed intake valve operation. Similarly, directlyinjected fuel may be delivered during an intake stroke, as well aspartly during a previous exhaust stroke, during the intake stroke, andpartly during the compression stroke, for example. As such, even for asingle combustion event, injected fuel may be injected at differenttimings from the port and direct injector. Furthermore, for a singlecombustion event, multiple injections of the delivered fuel may beperformed per cycle. The multiple injections may be performed during thecompression stroke, intake stroke, or any appropriate combinationthereof.

Fuel injectors 166 and 170 may have different characteristics. Theseinclude differences in size, for example, one injector may have a largerinjection hole than the other. Other differences include, but are notlimited to, different spray angles, different operating temperatures,different targeting, different injection timing, different spraycharacteristics, different locations etc. Moreover, depending on thedistribution ratio of injected fuel among injectors 170 and 166,different effects may be achieved.

Fuel tanks in fuel system 8 may hold fuels of different fuel types, suchas fuels with different fuel qualities and different fuel compositions.The differences may include different alcohol content, different watercontent, different octane, different heats of vaporization, differentfuel blends, and/or combinations thereof etc. One example of fuels withdifferent heats of vaporization could include gasoline as a first fueltype with a lower heat of vaporization and ethanol as a second fuel typewith a greater heat of vaporization. In another example, the engine mayuse gasoline as a first fuel type and an alcohol containing fuel blendsuch as E85 (which is approximately 85% ethanol and 15% gasoline) or M85(which is approximately 85% methanol and 15% gasoline) as a second fueltype. Other feasible substances include water, methanol, a mixture ofalcohol and water, a mixture of water and methanol, a mixture ofalcohols, etc.

Controller 12 is shown in FIG. 1 as a microcomputer, includingmicroprocessor unit 106, input/output ports 108, an electronic storagemedium for executable programs and calibration values shown asnon-transitory read only memory chip 110 in this particular example forstoring executable instructions, random access memory 112, keep alivememory 114, and a data bus. Controller 12 may receive various signalsfrom sensors coupled to engine 10, in addition to those signalspreviously discussed, including measurement of inducted mass air flow(MAF) from mass air flow sensor 122; engine coolant temperature (ECT)from temperature sensor 116 coupled to cooling sleeve 118; a profileignition pickup signal (PIP) from Hall effect sensor 120 (or other type)coupled to crankshaft 140; throttle position (TP) from a throttleposition sensor; and absolute manifold pressure signal (MAP) from sensor124. Engine speed signal, RPM, may be generated by controller 12 fromsignal PIP. Manifold pressure signal MAP from a manifold pressure sensormay be used to provide an indication of vacuum, or pressure, in theintake manifold. Controller 12 may infer an engine temperature based onan engine coolant temperature.

As described above, FIG. 1 shows only one cylinder of a multi-cylinderengine. As such, each cylinder may similarly include its own set ofintake/exhaust valves, fuel injector(s), spark plug, etc. It will beappreciated that engine 10 may include any suitable number of cylinders,including 2, 3, 4, 5, 6, 8, 10, 12, or more cylinders. Further, each ofthese cylinders can include some or all of the various componentsdescribed and depicted by FIG. 1 with reference to cylinder 14.

In some examples, vehicle 5 may be a hybrid vehicle with multiplesources of torque available to one or more vehicle wheels 55. In otherexamples, vehicle 5 is a conventional vehicle with only an engine. Inthe example shown, vehicle 5 includes engine 10 and an electric machine52. Electric machine 52 may be a motor or a motor/generator. Crankshaft140 of engine 10 and electric machine 52 are connected via atransmission 54 to vehicle wheels 55 when one or more clutches 56 areengaged. In the depicted example, a first clutch 56 is provided betweencrankshaft 140 and electric machine 52, and a second clutch 56 isprovided between electric machine 52 and transmission 54. Controller 12may send a signal to an actuator of each clutch 56 to engage ordisengage the clutch, so as to connect or disconnect crankshaft 140 fromelectric machine 52 and the components connected thereto, and/or connector disconnect electric machine 52 from transmission 54 and thecomponents connected thereto. Transmission 54 may be a gearbox, aplanetary gear system, or another type of transmission. The powertrainmay be configured in various manners including as a parallel, a series,or a series-parallel hybrid vehicle.

Electric machine 52 receives electrical power from a traction battery 58to provide torque to vehicle wheels 55. Electric machine 52 may also beoperated as a generator to provide electrical power to charge battery58, for example during a braking operation.

As described above, a vehicle may be adapted with a pressurized airinduction (PAI) system coupled to an engine to improve performanceduring operations demanding increased torque. A pressurized airinduction (PAI) system 200 is shown in FIG. 2 that may be coupled to anengine intake manifold 202. Elements that are common to elements of FIG.1 are similarly numbered. The engine intake manifold 202 may direct airflow to a plurality of cylinders, such as cylinder 14 of FIG. 1 , inwhich air may be mixed with fuel for combustion. The PAI system includesa first pathway 204 for delivering ambient air and a second pathway 206for delivering compressed, cooled air to intake manifold 202. Adirection of air flow through both the first pathway 204 and secondpathway 206 of the PAI system is indicated by arrows 210. Air may bereceived in the PAI system 200 via an intake passage 142, which may inone example be the air intake passage 142 of FIG. 1 . Air may then flowinto the first pathway 204 and/or continue along intake passage 142 intothe second pathway 206.

The first pathway 204 of PAI system 200 is coupled to the intake passage142 via a coupling, shown in this example as a T-body 212. Othercouplings, however, may be similarly used. The T-body 212 has a firstjunction 214 from which a bypass duct 216 of the first pathway 204extends. In one example, bypass duct 216 may be the bypass duct 194 ofFIG. 1 . The bypass duct 216 diverts air drawn from intake passage 142to intake plenum 146 while bypassing a compressor. As a result of thebypass duct, the first pathway 204 has a shorter length relative to thesecond pathway 206, enabling air at ambient pressure to be rapidlydelivered to the engine intake manifold 202 when required by increasingan opening of the first pathway 204. Thus first pathway 204 acts as ashortcut for supplying ambient air to the engine intake manifold 202during low engine loads and speeds where little or no boost is desired,e.g., following a tip-out. By supplying ambient air to the engine intakemanifold 202 that is not cooled prior to delivery, condensation withinthe first pathway 204 may be avoided.

The first pathway 204 may also include the first throttle 162 positionedat a downstream end of the bypass duct 216 that is distal relative tothe T-body 212 and proximal to the intake plenum 146 of the engineintake manifold 202. In one example, the first throttle 162 may controlflow through the first pathway 204 to the engine intake manifold 202based on signals received from controller 12. Controller 12 may commanda degree of opening to first throttle 162 based on input indicative oftorque demand, such as based on input from an accelerator pedal. Basedon the degree of opening of first throttle 162, an amount of air flowingthrough intake passage 142 may be drawn through the first junction 214of the T-body into bypass duct 216, and then delivered to engine intakemanifold 202 upon passage through first throttle 162. As such, the airdiverted into the first pathway 204 bypasses components included in thesecond pathway 206 that boost and cool the air contained therein.

The second pathway 206 is coupled to air intake passage 142 downstreamof T-body 212 via second junction 220. The second junction 220 may bearranged perpendicular to the first junction 214. In one example, thecoupling of the second pathway 206 to the first pathway 204 via theT-body may give PAI system 200 a Y-shaped structure. Specifically, byincorporating a T-body into intake passage 142 to couple the bypass duct216 to the intake passage, the PAI system 200 may have a Y-shape in theregion comprising intake passage 142, T-body 212, and bypass duct 216.

Air flowing into the PAI system 200 may flow through second junction 220of the T-body 212 before entering second pathway 206. Second pathway 206is a boosted air pathway including compressor 174 and CAC 192. In oneexample, compressor 174 is coupled in the turbocharger 175 and is drivenvia exhaust turbine 176.

Intake passage 142 extends into second pathway 206 downstream of thesecond junction 220 of the T-body 212 and is coupled to intake plenum146 downstream of compressor 174 and CAC 192. Second pathway 206 alsoincludes the second throttle 196 positioned at a downstream end ofsecond pathway 206 that is proximal to the intake plenum 146. The secondthrottle 196 may be actuated in a similar manner to the first throttle162 via instructions from the controller 12 in response to an inputdevice, such as the accelerator pedal. Delivery of air from the secondpathway 206 to the engine intake manifold 202 may be controlled byactuation of the second throttle 196 between a fully open and a fullyclosed position (to any position there-between). For example, when thereis an increase in torque demand and the engine is operated at a mid-highspeed-load region, the compressor 174 may be operated and the secondthrottle 196 may be opened to deliver the boosted air.

Second pathway 206 includes a first branch 222 defining a region ofsecond pathway 206 from downstream of junction 220 to an inlet of CAC192, and a second branch 224 defining a region of second pathway 206from an outlet of CAC 192 to a location where the second pathway iscoupled to intake plenum 146. Air flows through the second pathway 206in a downstream direction from second junction 220 of T-body 212 tocompressor 174, then through the PRV 164 before flowing into CAC 192.Air compressed via the compressor 174 is then cooled upon passagethrough CAC 192. Cooled compressed air then flows from CAC 192 intointake plenum 146 via second throttle 196.

Air flowing through intake passage 142 may first undergo compression bycompressor 174, hereafter referred to as boosted air, and subsequentlypass through PRV 164. PRV 164 may be a one-way valve that ensures thatthe boost pressure is contained on a downstream side of PRV 164, so thatreverse flow of boosted air through the second pathway 206 does notoccur. PRV 164 remains closed until a pressure threshold is exceeded.For example, the pressure threshold may be a non-zero pre-set valuebased on a safety rating of pressure allowance of the walls of the firstbranch 222 and second branch 224 or of fittings connecting the firstbranch 222 and second branch 224 to the CAC 192. In one example, thepressure threshold may be 14 Psi. When the boost pressure downstream ofPRV 164 exceeds a threshold, PRV 164 may open to release the pressure.Continuing along the path of air flow in second pathway 206, air mayflow through PRV 164 into first branch 222 and then flow through CAC192. In one example, CAC 192 may be coupled to an engine cooling circuitthat enables heat transfer from air, heated during compression, throughsurfaces of CAC 192 to a coolant. The heat exchange occurring at the CAC192 both cools the air and increases the density of the air flowingthrough CAC 192 that is eventually delivered to the engine intakemanifold 202, thereby improving the intake throttle response of theboosted engine. The flow of coolant through the CAC 192 may be variedbased on boosted engine operating conditions. For example, flow ofcoolant through CAC 192 may be enabled when the engine is operatingboosted, such as when compressor 174 is operated and second throttle 196is at least partially open. As another example, flow of coolant throughCAC 192 is disabled when the engine is operating without boost, such aswhen compressor 174 is not operated and second throttle 196 is heldclosed. By limiting operation of the CAC 192 to conditions when theengine is operating boosted, the engine's fuel economy may be improvedby minimizing wasteful operation of the CAC 192. In addition, componentlife of the CAC 192 is increased.

Upon exiting CAC 192, the cooled, boosted air enters the second branch224 of second pathway 206, and flows through second throttle 196. Thesecond throttle 196 controls the delivery of cooled, boosted air fromthe second pathway 206 into the intake plenum 146. The intake plenum 146then directs cooled, boosted air to the engine intake manifold 202 andthereon to the engine cylinders.

In addition to providing a pathway for boosted air when the secondthrottle is opened, the second pathway 206 may also function as areservoir of boosted air when the second throttle 196 is closed. Forexample, responsive to a tip-out following boosted engine operation, thesecond throttle 196 may be closed to retain compressed air within secondpathway 206 such as within at least the second branch 224 of the secondpathway 206. In this way, when the second throttle 196 is closed, thesecond pathway 206 may act as an air induction reservoir. During lightengine loads when boosted air is not required, the first throttle 162 isopened and the second throttle 196 is closed, enabling boosted air to bestored within PAI system 200. During a subsequent tip-in, the storedboosted air may be quickly delivered to the intake plenum 146 and thento the engine intake manifold 202 via the opening of second throttle196, while the compressor 174 is spooled up. In this way, the release ofthe stored air from the second pathway 206 reduces turbo lag.

As such, the boost supporting potential of the stored boosted air may beaffected by its temperature. Specifically, the release of coolcompressed air, stored in the second pathway 206 during a tip-out, andreleased from the second pathway 206 during a subsequent tip-in, mayreduce turbo lag as long as the compressed air is sufficiently cool.However, when the second pathway 206 is in a passive state while holdinga reservoir of boosted air and with cooling operation of the CAC 192disabled, heat may be transferred to the stored air. The amount of heattransferred may be determined as a function of ambient conditions. Forexample, as the ambient temperature rises, and/or the ambient humidityrises, the amount of heat transferred from the ambient air surroundingthe PAI system 200 to the cool compressed air retained in the secondpathway 206 may increase. Warming of the boosted air may reduce thedensity of the air, reducing the throttle response of the boosted airwhen it is released, and thereby lowering the amount of boost that itcan provide. Accordingly, the PAI system 200 may be adapted to vent thestored boosted air from the second pathway 206 when a temperature ortime threshold is exceeded, independent of the torque demand.

For example, while the second throttle 196 is closed, the controller mayestimate or infer the amount of heat being transferred to the storedair. In one example, the output of an intake air humidity sensor 230 andan intake air temperature (IAT) sensor 232 arranged along intake passage142, upstream of the T-body 212 may be used to estimate ambient humidityand ambient temperature, respectively, when the second throttle 196 isclosed. Based on the measured ambient conditions, the controller maycalculate an amount of heat transferred to the stored boosted air, arate of rise in temperature, and an inferred boosted air temperature.The inferred boosted air temperature may be additionally or optionallydetermined as a function of the boosted air temperature at the time thesecond throttle 196 was closed, as well as a duration elapsed since thesecond throttle 196 was closed. In one example, the controller may use amodel or algorithm to infer the temperature of the boosted air retainedin the second pathway 206, in real-time. If the inferred temperature ofthe stored air exceeds a threshold before a subsequent tip-in event isconfirmed, the controller may actuate the second throttle 196 to atleast a partially open position to discharge the stored air to theengine while still at low engine speeds or loads. In one example, thesecond throttle 196 may be transiently shifted to a fully open positionto release the stored air, and then returned to the closed position. Anopening of the first throttle 162 may be adjusted based on the transientopening of the second throttle 196, as elaborated at the method of FIG.5 . In addition, one or more engine operating parameters, such as sparktiming, may be adjusted to reduce torque transients associated with therelease of the warm compressed air into the engine intake manifold 202.

In the depicted example, each of first throttle 162 and second throttle196 may be equipped with an actuating mechanism that receives separatesignals from the controller 12. This allows the two throttles to beoperated independently. A detailed embodiment of a PAI system 200 withdistinct throttles is shown with reference to FIGS. 3A-3B.Alternatively, a single actuating mechanism may control the opening andclosing of both the first throttle 162 and second throttle 196, inconcert. In yet another embodiment, as detailed with reference to FIGS.4A-4B, air flow to the engine from the first pathway 204 and secondpathway 206 may be controlled by a single splitter valve arranged in theintake plenum 146 in a merging region 226 of the bypass duct 216 andsecond branch 224 of the second pathway 206. In this arrangement, airdelivered via the first pathway and/or the second pathway issimultaneously controlled by a single valve with dimensions optimizedfor the geometry at the merging region 226 of the intake plenum 146.Embodiments illustrating the use of the throttles (FIGS. 3A-3B) and thesplitter valve (FIGS. 4A-4B) for directing air flow to the engine arefurther described in detail below.

A first embodiment 300 of a PAI system, such as of PAI system 200 ofFIG. 2 , is illustrated at FIGS. 3A-3B. A set of reference axes 304 isprovided for comparison between views, indicating a “z” lateraldirection, “x” horizontal direction, and “y” vertical direction. FIG. 3Adepicts a top view 350 of the first embodiment 300 of PAI system 200.The first and second pathways, with reference to the first and secondpathways 204 and 206 of FIG. 2 , are cut-off upstream of the firstthrottle 162 along line A-A′ and upstream of the second throttle 196along line B-B′ to provide the view shown in FIG. 3A. The first throttle162 couples to a downstream end of the bypass duct 216 of the firstpathway 204 and the second throttle 196 couples a downstream end of thesecond branch 224 of the second pathway 206, with reference to FIG. 2 .The bypass duct 216 and second branch 224 merge in the intake plenum 146at the merging region 226. The intake plenum 146 is connected to anintake manifold 302 of a vehicle, such as vehicle 5 of FIG. 1 .

The bypass duct 216 and second branch 224 merge so that the mergingregion 226 is Y-shaped. Air flowing into the intake manifold 302 fromeither the first bypass duct 216 or second branch 224, or simultaneouslyfrom both, is directed into a merged channel 303, e.g. the stem of theY-shape, of the intake plenum 146 before entering the engine intakemanifold 302. When ambient air enters the intake plenum 146 from bypassduct 216 and boosted air enters via the second branch 224, the two typesof air are mixed within the merged channel 303 of the intake plenum 146before flowing to the engine intake manifold 302. In this way, the airentering the engine intake manifold 302 may have a temperature andpressure determined by the proportional mixing of the warmer, ambientair and the cooler, boosted air.

A view 360, taken from a direction along the second branch 224 of thesecond pathway 206, of the first and second throttles 162 and 196depicted in FIG. 3B shows that the first throttle 162 and secondthrottle 196 may block the flow of air by extending a first sealing wall317 entirely across a first opening 316 in the first throttle 162.Similarly, flow through the second throttle 196 may be blocked byextending a second sealing wall 319 entirely across a second opening318. The first sealing wall 317 and second sealing wall 319 may beadjustable so that the first opening 316 and second opening 318,respectively, may be partially open. For example, the first sealing wall317 may extend a portion across the first opening 316 in the firstthrottle 162, and similarly the second sealing wall 319 may extend aportion across the second opening 318 of the second throttle 196 wherethe portion may include 1-99% of the area of the first and secondopenings 316 and 318. In other words, the first opening 316 of firstthrottle 162 and the second opening 318 of second throttle 196 may bereduced from fully open positions so that the first sealing wall 317does not extend entirely across the first opening 316, and the secondsealing wall 319 does not extend entirely across the second opening 318.

Based on engine speed and operation, a signal may be sent to each offirst throttle 162 and second throttle 196 from a controller to adjustthe first opening 316 and second opening 318, respectively. During lowengine speeds and operating loads, the first throttle 162 is actuated toan open position, e.g., fully open, while the second throttle 196 isconcurrently actuated to a closed position, e.g., fully closed, so thatfresh air may be delivered via the first pathway 204. Conversely, duringhigh engine speeds and heavy operating loads, the first throttle 162 maybe fully closed and the second throttle 196 fully opened so that cooled,boosted air may be delivered exclusively via the second pathway 206.Furthermore, detection of a tip-out may result in either a fully open orpartially open position of the first throttle 162 while the secondthrottle is fully closed. Subsequent to the tip-out and independent oftorque demand, if a time or temperature threshold calculated for thestored boosted air is surpassed, the reservoir of boosted air isdischarged. Therein, the first throttle 162 may receive a signal tofully close or reduce the first opening 316 as the second throttle 196is simultaneously actuated to at least a partially open position. Airfrom both the first pathway 204 and second pathway 206 are thusdelivered to the merged channel 303 of the intake plenum 146 and mixedtherein before flowing to the engine intake manifold 302.

As discussed above, the air flow in the PAI system may be controlled byeither a pair of throttles, one disposed in each of the first and secondpathways, or by a splitter valve. A second embodiment of a PAI system400 is illustrated at FIGS. 4A-4B. Only an intake plenum 440 isdepicted, which may be an embodiment of intake plenum 146 of FIG. 1 ,showing the coupling of a splitter valve 401 to the intake plenum 440.The intake plenum 440 has a first duct 450 that may couple to a firstpathway of the PAI system 400 that flows ambient air and a second duct452 that may couple to a second pathway that delivers cooled boostedair. Air may enter each the of the first duct 450 and the second duct452 in the directions indicated by arrows 410 and exit from the intakeplenum 440 through a single channel 403 into which the first duct 450and second duct 452 merge. The single channel 403 may direct air flowinto an engine intake manifold, such as engine intake manifold 202 ofFIG. 2 .

The intake plenum 440 is viewed from above in FIG. 4A while across-section of the intake plenum 440, taken along the plane formed bythe “z” lateral direction and “x” horizontal direction, is shown in FIG.4B. In the embodiment of FIGS. 4A-4B, the first throttle 162 and secondthrottle 196 of FIGS. 3A-3B are replaced by a single splitter valve 401.The splitter valve 401 may provide a single mechanism for adjusting theflow through each of the first and second pathway of the PAI system 400,in contrast to the separate mechanisms and control of the example PAIsystem 200 shown in FIGS. 3A-3B.

The splitter valve 401 splits flow between the first ducts 450 andsecond duct 452 of the intake plenum 440, thus acting as a singleproportioning valve instead of two separate adjustable bodies, e.g. thefirst and second throttles 162 and 196 of FIGS. 3A-3B. Based on aposition of the valve, the splitter valve 401 may enable flow throughthe first duct 450 exclusively, the second duct 452 exclusively, or froma combination of both the first and second duct 450 and 452. The amountof flow from each of the first and second ducts 450 and 452 relative toone another may be controlled by an actuator 402 of the splitter valve401 based on a command signal received from an engine controller.

An outer portion 420 of the splitter valve 401 (e.g., the portion thatis positioned outside of the intake plenum 440), may include an actuator402 that is in electronic communication with the controller, such ascontroller 12 of FIG. 1 , and an arm 404. The actuator 402 may bearranged adjacent to a single channel 403 into which the first duct 450and second duct 452 merge. At a first end 409 of the actuator 402 thatis upstream of a second end 411, the actuator 402 is connected to thearm 404. The actuator 402 receives signals that may be translated intomovement of the arm 404.

The arm 404 extends across the second duct 452, in a directionperpendicular to air flow, as indicated by arrows 410, and may be fixedto a wall of the intake plenum 440 in a saddle 412, where the first duct450 and second duct 452 meet, via a pin 414. The pin 414 extends througha wall 418 of the intake plenum 440. The arm 404 comprises a pluralityof sections 406 connected by hinges 408 around which the plurality ofsections 406 may be pivoted. The pivoting of the plurality of sections406 of the arm 404 may rotate a V-shaped splitter 416 arranged insidethe intake plenum 440, as shown in FIG. 4B.

The V-shaped splitter 416 has a first flap 415 positioned inside thefirst duct 450 which has a first central axis 405 and a second flap 417positioned inside the second duct 452 which has a second central axis407. The first central axis 405 is arranged perpendicular to the secondcentral axis 407. The first flap 415 and second flap 417 may beconnected to one another at a fulcrum defined by the position of the pin414. The pin 414, extending through the wall 418, may connect to theV-shaped splitter 416 at the fulcrum inside the intake plenum 146,securing valve 416 to the saddle 412 at the fulcrum of the V-shape.Rotation of the pin 414 by the arm 404 may also rotate the V-shapedsplitter 416.

The first flap 415 and second flap 417 may be at a fixed angle 419relative to one another. The fixed angle 419 may be greater than 90degrees or less than 90 degrees, but not 90 degrees in order to allowgreater flow through of the first duct 450 than the second duct 452 orgreater flow through the second duct 452 than the first duct 450 to theengine intake manifold by pivoting the V-shaped splitter 416 via the pin414. When either the first flap 415 or the second flap 417 is arranged90 degrees within the first duct 450 and second duct 452, respectively,the duct is sealed.

As an example, during conditions when more flow through the first duct450 than the second duct 452 is desired, such as at low loads, theV-shaped splitter 416 may pivot so that the second flap 417 is slightlymore or less than perpendicular to the second central axis 407. Asmaller opening in the second duct 452 due to the near perpendicularpositioning of the second flap 417 (in comparison to the first flap 415which deviates further from perpendicular), allows more air flow throughthe first duct 450 than the second duct 452. In another example, if onlyflow through the first duct 450 is desired, adjusting the V-shapedsplitter 416 so that the second flap 417 is perpendicular to the secondcentral axis 407 may entirely close the second duct 452 while allowingthe first flap 415 to remain open, thereby enabling exclusive flowthrough the first duct 450. To enable more flow through the second duct452 than the first duct 450 during higher engine loads and speeds, theV-shaped splitter 416 may pivot so that the first flap is slightly moreor less than perpendicular to the first central axis 405. This resultsin a larger opening in the second duct 452 than the first duct 450. Forexclusive flow from the second duct 452, the V-shaped splitter 416 maybe adjusted so that the first flap 415 is perpendicular to the firstcentral axis 405. The first duct 450 is thus closed and air is deliveredto the intake plenum 440 through the second duct 452.

Now turning to FIG. 5 , example routines 500 for supplying eitherambient air or cool, boosted air to an engine is described. Boosted airmay be discharged from a reservoir of a PAI system in response to anincrease in torque demand and engine operation in a higher enginespeed-load region (such as following an operator pedal tip-in event)requesting additional engine torque and/or a tip-out (e.g. pedalreleased). By adjusting the air flow from a first pathway and/or asecond pathway of the PAI system, cooled, boosted air may be stored inthe PAI system and supplied to the engine as desired. Instructions forcarrying out method 500 and the rest of the methods included herein maybe executed by a controller based on instructions stored on a memory ofthe controller and in conjunction with signals received from sensors ofthe engine system, such as the sensors described above with reference toFIG. 1 . The controller may employ engine actuators of the engine systemto adjust engine operation, according to the methods described below.

At 502, the operating conditions of the engine may be estimated and/ormeasured. These may include, for example, engine speed and load, torquedemand, engine coolant temperature, barometric pressure, ambienthumidity, ambient temperature, MAP, MAF, etc. At 504, it may bedetermined if there is an increase in operator torque demand. Forexample, it may be determined whether an accelerator pedal tip-in isdetected. In one example, accelerator pedal depression may be measuredvia a pedal position sensor. If no tip-in is detected, at 506, themethod includes operating at nominal settings based on the estimatedengine parameters.

In one example, where the engine is operating at low-mid speed-loads,operating at nominal conditions includes supplying fresh air to enginecylinders at ambient temperature, pressure, and humidity via the firstpathway of the PAI system while maintaining the second pathway, thatincludes a compressor and a CAC, closed. This includes opening the firstpathway by actuating a first throttle disposed in the first pathwayproximal to an intake plenum coupled to an engine intake manifold toeither a fully open position or partially open position. Partiallyopening the first throttle may comprise adjusting an opening of thefirst throttle to be a percentage of the opening when fully open. Forexample the opening of the partially open first throttle may be 20%,50%, 70% or a percentage between 1%-99% relative to the opening of thefirst throttle when the first throttle is fully open.

If a tip-in is detected, the method proceeds to 508 where the controllermay send a signal to decrease flow through the first pathway andincrease flow through the second pathway of the PAI system so that alarger portion of the air delivered to the engine intake is cooled,boosted air. The routine includes directing ambient air from an intakepassage through the compressor of a turbocharger and then cooling theair through the CAC so that the air is cooled and compressed uponreaching the engine intake. In one example, where the PAI system has afirst throttle coupled to a first pathway and a second throttle coupledto a second pathway, directing a larger portion of air to the engine asboosted air includes opening the second throttle and closing the firstthrottle. The degree of opening of the second throttle is based on anamount of torque requested, as inferred from the pedal position. Themore the pedal is depressed, the greater the torque demanded, resultingin a higher degree of opening of the second throttle. The secondthrottle may open by a smaller amount when the pedal is slightlydepressed or fully open when the pedal is depressed to a maximum.Concurrent with the opening of the second valve, the first valve openingis decreased as input from the pedal indicates increase in demand forboosted air. The first valve opening may decrease by a proportionaldegree to the amount the second valve is opened or the first valve maybe fully closed to avoid potential change in pressure and/or temperatureof the boosted air due to mixing with ambient air.

In another example, where the PAI system has a splitter valve disposedin a region where the first pathway and second pathway merge with afirst flap arranged in the first pathway and a second flap arranged inthe second pathway, operating at nominal conditions at 506, as describedabove, includes adjusting the splitter valve so that the second flap isperpendicular to the path of flow in the second pathway. The secondpathway is thus closed and the first pathway is open, delivering ambientair to the engine via the first pathway of the PAI system.

In the event of a tip-in, the method at 508 directs a larger portion ofair to the engine as boosted air. The splitter valve may be tilted sothat the second flap forms an opening in the second pathway that islarger than an opening formed by the first flap in the first pathway.The angling of the splitter valve is based on an amount of torquerequested, e.g. sensing of pedal position. The more the pedal isdepressed, the greater the torque demanded, resulting in adjustment ofthe splitter valve so that the first flap is closer to perpendicular inthe first pathway than the second valve. The closer the first flap is toperpendicular, the smaller the opening in the first pathway relative tothe opening in the second pathway. If a small depression in pedalposition is detected, the splitter valve may tilt so that the first flapis slightly closer to perpendicular within the first pathway than thesecond flap within the second pathway. As a result, a smaller opening isformed in the first pathway than the second pathway. If the pedal isdepressed to a maximum position, the first flap may be positionedexactly perpendicular so that the first pathway is blocked and airdelivered to the engine is entirely boosted air from the second pathway.

At 510, air is drawn through the second pathway from an intake passage,such as intake passage 142 of FIG. 2 , pressurized by the compressor andthen cooled upon passing through the CAC. At 512 the method maydetermine if a tip-out is detected, e.g., if the accelerator pedal isreleased as inferred by the pedal position sensor. If the tip out is notdetected, engine operation continues to 514 with the second pathway openand the first pathway while torque demand remains elevated. If a tip-outis detected, the method proceeds to 516 where the controller may send asignal to increase flow through the first pathway and decrease flowthrough the second pathway of the PAI system so that a larger portion ofthe air delivered to the engine intake is ambient air.

In one example, where the PAI system has a first throttle coupled to afirst pathway and a second throttle coupled to a second pathway,directing a larger portion of air to the engine as ambient air includesopening the first throttle and closing the second throttle. The degreeof opening of the first throttle and closing of the second throttle isbased on the torque demand. The more the pedal is released, e.g. lessdepressed, the lower the torque demand resulting in the furtherreduction of the opening of the second throttle. The lower torquedemand, as inferred by pedal position, and the consequent decrease inthe opening of the second throttle results in an increase in the openingof the first throttle. When the pedal is fully released, the firstthrottle may be fully opened while the second throttle is fully closed.

In another example, where the PAI system has a splitter valve disposedin a region where the first pathway and second pathway merge with afirst flap arranged in the first pathway and a second flap arranged inthe second pathway. At 516, the splitter valve may be tilted so that thefirst flap forms an opening in the first pathway that is larger than anopening formed by the second flap in the second pathway. The angling ofthe splitter valve is based the decrease in torque demand, inferred bythe pedal position. The less the pedal is depressed, the lower thetorque demanded, resulting in adjustment of the splitter valve so thatthe second flap is closer to perpendicular in the second pathway thanthe first valve. The closer the second flap is to perpendicular, thesmaller the opening in the second pathway relative to the opening in thefirst pathway. If the pedal is released, for example, to a half-waydepressed position, the splitter valve may tilt so that the second flapis slightly closer to perpendicular within the second pathway than thefirst flap within the first pathway. As a result, a smaller opening isformed in the second pathway than the first pathway. If the pedal fullyreleased, the second flap may be positioned exactly perpendicular sothat the second pathway is blocked and air delivered to the engine isentirely ambient air from the first pathway.

At 518, ambient air is flowed at barometric pressure to the engineintake, bypassing the compressor and CAC. While ambient air is drawninto the engine, flow through the second pathway is blocked by closingthe second throttle or second flap of the splitter valve. The aircontained within the second pathway is trapped at 519 between a PRV,such as PRV 164 of FIG. 2 , at an upstream end and the second throttleor second flap at a downstream end of the second pathway at 519. Withinthe closed second pathway, the air trapped upstream of the CAC may bepressurized and at ambient temperature while the air trapped downstreamof the CAC may be pressurized and cooled. At 520, the state of thestored boosted air in the second pathway is estimated by inferring anamount of heat transferred to the stored air and calculating a rate oftemperature rise.

For example, data from an intake humidity sensor and an IAT sensor, suchas the sensors 230 and 232 of FIG. 2 , may be sent to the controller toestimate the ambient humidity and ambient temperature of the trappedair. The data is used to calculate, based on information stored in thecontroller about conductivity of the material forming the walls of thesecond pathway and the temperature differential between ambient air andtrapped boosted air, the amount of heat transfer from the surroundingair external to the second pathway into the trapped air. The heattransfer may be used to determine a temperature of the trapped air whichis compared to a pre-set non-zero temperature threshold. The thresholdmay be a temperature at or above which the boost potential of thetrapped air is reduced to an extent that the boosted performance of theengine may be degraded if the trapped air is discharged. In addition tothe temperature threshold, a time threshold may be used to evaluate theboost potential of the stored air.

A rate of temperature rise, e.g., joules per second, of the trapped airmay be inferred from the estimated heat transfer. The time threshold maybe calculated based on a look-up table stored in a memory of thecontroller providing time thresholds as a function of ambient conditionsand estimated rate of temperature rise. For example, low ambienttemperatures or low ambient humidity may result in slower rates oftemperature rise, a longer time threshold, and a longer period of timebefore the temperature of the trapped air reaches or exceeds thetemperature threshold. Conversely, high ambient temperature or highambient humidity may shorten the time threshold due to a faster expectedrate of temperature rise. Both the pre-set temperature threshold as wellas the time threshold may be used to evaluate the state of the trappedboosted air in the second pathway of the PAI system.

At 522 of method 500, the inferred temperature of the stored air and theduration since the second pathway was closed to trap the boosted air maybe compared to the pre-set thresholds stored in the memory of thecontroller. If the estimated temperature is not above the temperaturethreshold or the duration of time does not exceed the calculated timethreshold, air is maintained trapped within the second pathway. Themethod then determines if a tip-in is detected at 526. In the event thatno tip-in is detected, the method returns to 520 and evaluates the stateof the trapped air based on ambient temperature and humidity asdescribed above, followed by comparison with pre-set thresholds at 522.Alternatively, if a tip-in is detected, the method returns to 508 wherean opening of the first pathway is decreased and an opening of thesecond pathway is increased based on the pedal position detected andinferred demand for torque. Ambient air is delivered to the engine whileflow of boosted air is minimized or blocked.

Returning to 522 of method 500, if the heat transfer exceeds thethreshold, the method proceeds to 530. At 530, the second pathway isopened to allow the warmed boosted air to be discharged to the engineintake manifold. The release of warmed boosted air, however, in additionto the air delivered to the engine intake manifold via first pathway mayresult in boosting the engine above a desired level of torque.Consequently, the controller may send a signal to reduce the flow ofambient air from the first pathway.

In one example, where the PAI system has a first throttle coupled to afirst pathway and a second throttle coupled to a second pathway, openingthe second pathway to discharge the stored boosted air includes openingthe second throttle and closing the first throttle. The degree ofopening of the second throttle and closing of the first throttle isbased on the amount of torque requested, as inferred from pedalposition. For example, if the pedal is slightly depressed, the firstthrottle may be fully closed and the second throttle partially opened toprevent the engine from becoming overloaded. If the pedal is halfwaydepressed, the opening of first throttle may be reduced but stillpartially opened while the second throttle is partially opened to ventthe stored air.

In another example, where the PAI system has a splitter valve disposedin a region where the first pathway and second pathway merge with afirst flap arranged in the first pathway and a second flap arranged inthe second pathway, opening the second pathway to discharge the storedboosted air includes tilting the splitter valve so that an opening inthe second path formed by the second flap is increased whilesimultaneously reducing the opening in the first pathway formed by thefirst flap. The angling of the splitter valve is based on the amount oftorque requested, as inferred from pedal position. For example, if thepedal is slightly depressed, the splitter valve may tilt so that theopening in the second pathway is smaller than the first pathway. If thepedal is halfway depressed, the splitter valve may be adjusted so thatthe openings in the first pathway and second pathway are approximatelyequal.

One or more engine actuators may be adjusted at 532 if decreasing theflow from the first pathway does not sufficiently compensate for theboost provided by the warmed boosted air. If a torque transient isexpected, other engine operating parameters may also be varied. Forexample, spark timing may be retarded, fuel injection and valve timingsmay be modified, or the ratio of fuel delivered via direct injectionversus port injection may be adjusted. By altering engine operations inresponse to excessive boost relative to engine load, misfiring at aplurality of cylinders of the engine may be avoided.

In one example, the degree to which spark timing is delayed is based ona difference between the amount of torque requested and an amount oftorque supplied. Upon discharging warmed, boosted air to the enginethrough the second pathway with flow from the first pathway reduced, theboosted air may still provide boost pressure to the engine beyond therequested amount inferred by the pedal position. As a result, spark maybe retarded from maximum brake torque (MBT) to avoid engine knock. Forexample the greater the discrepancy between the requested boost and theprovided boost, where the provided boost is too high, the longer thespark timing may be delayed to allow the pressure in a combustionchamber of the engine to dissipate by an amount before ignition. Inother words, the more the opening of the second pathway is increasedduring discharge of the warmed, stored air, the further the spark timingis retarded from MBT. When the supply of torque decreases to match thetorque demand spark timing then returns MBT.

Following the adjustment of engine operating parameters, the methodreturns to 526 to determine if a tip-in is detected. If no tip-in isdetected, the method returns to 520 and evaluates the state of thetrapped air based on ambient temperature and humidity as describedabove, followed by comparison with pre-set thresholds at 522.Alternatively, if a tip-in is detected, the method returns to 508 wherean opening of the first pathway is decreased and an opening of thesecond pathway is increased based on the pedal position detected andinferred demand for torque. Ambient air is delivered to the engine whileflow of boosted air is minimized or blocked. Thus, subsequent to initialstartup, boosted air may be readily supplied to the engine upondetection of a tip-in by discharging stored boosted air through thesecond pathway and decreasing flow through the first pathway. In theevent of a tip-out, the second pathway is bypassed, providing ashortened delivery path of ambient air to the engine, thereby avoidingthe unnecessary use of boosted air. During the tip-out, if thetemperature of the stored air surpasses a temperature threshold or aperiod of time elapses that exceeds a time threshold that renders thestored air less effective for providing boost, the stored air isreleased.

Example operations of a PAI system, with reference to the PAI system ofFIGS. 3A-3B are now discussed with reference to FIG. 6 . FIG. 7 shows anexample of a PAI system adapted with a splitter valve, as shown in FIGS.4A-4B. Based on a request for engine torque and on heat exchange to thestored boosted air in the PAI system, air flow through a first pathway,supplying fresh air, and a second pathway, supplying boosted air, isadjusted.

FIG. 6 shows an example operation of the PAI system adapted with a firstthrottle, controlling flow of fresh air, and a second throttle,controlling flow of boosted air. As elaborated in map 600, a tip-in ortip-out is detected by a pedal position, depicted in graph 602. Theopening and closing of the first and second throttle is shown at graph604 and graph 606, respectively. The temperature of the boosted air inthe second pathway, is illustrated at graph 608 and the boost pressureof the air supplied to the engine intake is shown at graph 610. Thespark timing is depicted in graph 612 as a function of the operatingconditions shown.

Prior to t1 the engine is operating at low speed with the first throttleopen, enabling the flow of fresh air through the first pathway to theengine. The second throttle is closed, blocking flow from the secondpathway into the engine since boost air is not required, a CAC is notoperating and the air temperature within the second pathway is close toambient temperature and above a pre-set, non-zero temperature threshold609. The boost pressure, as a result of the low torque demand, is alsolow and the spark timing is at or around MBT.

At t1, a tip-in is detected as indicated by a depression of anaccelerator pedal. The tip-in activates the adjustment of the air flowto the engine: the first throttle is entirely closed and the secondthrottle is entirely open. As air flows through the second pathway, theair is continually cooled, resulting in a gradual decrease in the airtemperature of the second pathway. The boost pressure in the secondpathway increases to meet the request for increased torque while thespark timing remains at MBT.

A tip-out, detected by reduced depression of the pedal, occurs at t2.Responsive to the tip-out, the first throttle is opened and the secondthrottle is closed, alternating the air supply to the engine to flowfresh air instead of boosted air. As a result of the closing of thesecond throttle, boosted air is stored in the second pathway. Between t2and t3, the stored air gradually warms due to heat transfer betweenambient air surrounding the second pathway and the air stored within thesecond pathway. Boost pressure of the stored air remains relativelyconstant until t3 when the temperature of the second pathway exceeds thetemperature threshold 609. The threshold may be a value above which theboost provided by the air is degraded. In addition, a time threshold mayelapse by t3 that is based on a rate of temperature rise calculated frominferred heat transfer and determines when the temperature of the storedair exceeds the temperature threshold 609. Responsive to the detectedsurpassing of the temperature and time thresholds described above, astep-wise adjustment of the opening of the second throttle is performed.Opening of the second throttle increases air flow to the engine, causingan undesired increase in torque. Thus the first throttle is adjusted tobe less open in association with the opening of the second throttle. Theboosted air in the second pathway, however, is pressurized so that witheach incremental opening of the second throttle, more air may flow outof the second pathway than an equal incremental closing of the firstthrottle. Thus, as shown in map 600 by graphs 604 and 606, each openingstep of the second throttle is accompanied by a larger step of the firstthrottle to accommodate the different densities of fresh air versusboosted air. As an example, for every 5% opening of the second throttlethe first throttle is closed by an estimated 15%.

The adjustment of the first and second throttle may not be able to fullycompensate for the increase in air flow to the engine via the secondpathway. As a result, a torque transient may occur with excess torquebeing produced. To address this, one or more engine operating parametersmay be adjusted. For example, spark timing may be retarded from MBT. Att3, spark ignition timing is retarded further from MBT as the secondthrottle opening is increased. A concurrent decrease in boost pressureis observed as the boosted air is released from the second pathway tothe engine while the air temperature in the second pathway remainsrelatively constant and above the temperature threshold 609.

At t4, a second tip-in is detected and the first throttle is closed asthe second throttle is opened. As air flows through the compressor andCAC operation in the second pathway is enabled, the air is cooled andthe temperature of the boosted air in the second pathway decreases belowthe threshold 609. The boost pressure at t4 is lower than the boostpressure following the first tip-in between t2 and t3 but higher thanthe initial period up to t1. The distance between the dashed line of t1and dashed line of t2 indicate a time for boost pressure to increasefrom pre-tip-in pressure at t1 to maximum boost pressure at t2, or turbolag. Similarly, the distance between the dashed line of t4 and dashedline of t5 indicates turbo lag before boost pressure increases tomaximum boost pressure following the tip-in at t4. Turbo lag followingthe second tip-in at t4 is shorter than turbo lag following the firsttip-in at t1. This shows a faster increase to maximum boost pressure bymaintaining a reservoir of boosted air stored in the second pathway ofthe PAI system. After t4, spark timing returns to MBT as air supply tothe engine is now appropriate relative to the torque demand.

In FIG. 7 , a similar set of operations as described in FIG. 6 are shownfor a PAI system adapted with a splitter valve, for example, thesplitter valve 401 of FIG. 1 . A tip-in or tip-out is detected by apedal position, depicted at graph 702. The position of the V-shapedvalve of the splitter valve is indicated at graph 704. The V-shapedvalve may be pivoted so that more ambient air, from the first pathway,is delivered to the engine than boosted air, from the second pathway, oradjusted so that more boosted air is delivered than ambient air. Amiddle position where the air flow to the engine comprising equalportions of ambient air from the first pathway and boosted air from thesecond pathway is represented by a dashed line 705. The V-shaped valvemay also be positioned so that air flows exclusively from the firstpathway or the second pathway. The temperature of the boosted air in thesecond pathway, is illustrated at graph 706 and the pressure of theboosted air supplied to the engine intake is shown at graph 708. Thespark timing is depicted at graph 710 as a function of the operatingconditions shown.

Prior to t1 the engine is operating at low speed with the splitter valveangled so that a first flap in the first pathway forms an opening,enabling the flow of fresh air through the first pathway to the engine.A second flap of the splitter valve is positioned perpendicular in thesecond pathway, blocking flow from the second pathway into the enginesince boost air is not required. The CAC is not operating and the airtemperature within the second pathway is close to ambient temperatureand above a pre-set, non-zero temperature threshold 709. The boostpressure, as a result of the low torque demand, is also low and thespark timing is at or around MBT.

At t1, a tip-in is detected as indicated by a depression of anaccelerator pedal. The tip-in activates the adjustment of the air flowto the engine: the first flap is perpendicular, blocking flow throughthe first pathway and the second pathway is open. As air flows throughthe second pathway, the air is continually cooled, resulting in agradual decrease in the air temperature of the second pathway. The boostpressure in the second pathway increases to meet the request forincreased torque while the spark timing remains at MBT.

A tip-out, detected by reduced depression of the pedal, occurs at t2.Responsive to the tip-out, the splitter valve is tilted so that thefirst pathway is opened and the second pathway is closed, alternatingthe air supply to the engine to flow fresh air instead of boosted air.As a result of the closing of the second pathway, boosted air is storedin the second pathway. Between t2 and t3, the stored air gradually warmsdue to heat transfer between ambient air surrounding the second pathwayand the air stored within the second pathway. Boost pressure of thestored air remains relatively constant until t3 when the temperature ofthe second pathway exceeds the temperature threshold 709.

The threshold may be a value above which the boost provided by the airis degraded. In addition, a time threshold may elapse by t3 that isbased on a rate of temperature rise calculated from inferred heattransfer and determines when the temperature of the stored air exceedsthe temperature threshold 709. Responsive to the detected surpassing ofthe temperature and time thresholds described above, a gradualadjustment of the position of the splitter valve is performed. Openingof the second pathway is increased while flow through the first pathwayis decreased, causing an undesired increase in torque. Thus the splittervalve is adjusted so that the opening in the first pathway is largerthan the opening in the second pathway to regulate the amount ofadditional air delivered to the engine. For example, the splitter valvemay be angled so that 80% of the air flow to the engine is ambient airfrom the first pathway while 20% of the air flow is boosted air from thesecond pathway. As shown in map 700 by graphs 704 and 706, the splittervalve position is biased towards the first pathway immediately after t3and is gradually adjusted towards the middle position, indicated bydashed line 705 with the first pathway slightly more open than thesecond pathway until t4.

The adjustment of the splitter valve may not be able to fully compensatefor the increase in air flow to the engine via the second pathway. As aresult, a torque transient may occur with excess torque being produced.To address this, one or more engine operating parameters may beadjusted. For example, spark timing may be retarded from MBT. At t3,spark timing is retarded further from MBT as the flow through the secondpathway is increased. A concurrent decrease in boost pressure isobserved as the boosted air is released from the second pathway to theengine while the air temperature in the second pathway remainsrelatively constant and above the temperature threshold 609.

At t4, a second tip-in is detected and the splitter valve is angled sothat first pathway is closed as the second pathway is opened. As airflows through the compressor and CAC operation in the second pathway isenabled, the air is cooled and the temperature of the boosted air in thesecond pathway decreases below the threshold 709. The boost pressure att4 is lower than the boost pressure following the first tip-in betweent2 and t3 but higher than the initial period up to t1. The distancebetween the dashed line of t1 and dashed line of t2 indicate a time forboost pressure to increase from pre-tip-in pressure at t1 to maximumboost pressure at t2, or turbo lag. Similarly, the distance between thedashed line of t4 and dashed line of t5 indicates turbo lag before boostpressure increases to maximum boost pressure following the tip-in at t4.Turbo lag following the second tip-in at t4 is shorter than turbo lagfollowing the first tip-in at t1. This shows a faster increase tomaximum boost pressure by maintaining a reservoir of boosted air storedin the second pathway of the PAI system. After t4, spark timing returnsto MBT as air supply to the engine is now appropriate relative to thetorque demand.

In this way, boosted air may be stored in a PAI system so that boost isreadily available during an increase in engine load. By discharging thestored air during a tip-in while a compressor spools up, turbo lag isreduced. By including an air pathway that bypasses a compressor and CAC,ambient air can be rapidly provided to the engine at low loads.Furthermore, when the stored air is warmed above a threshold and haslower boosting ability, the stored air is can be vented. The technicaleffect of coupling the PAI system to an engine is that turbo lag isminimized when higher engine torque is requested by maintaining a supplyof cool, boosted air in the ducting.

As an embodiment, a boosted engine method includes: at higher engineload, drawing cool compressed air into an engine via an air intakepassage; at lower engine load, drawing ambient air into the engine via aduct while retaining cooled compressed air in the air intake passage;and releasing the compressed air from the air intake passage based onheat transferred to the compressed air during the lower engine load. Ina first example of the boosted engine method, estimating the heattransferred to the compressed air retained in the air intake passage isbased on ambient conditions including ambient temperature and humidity,the heat transferred is increased as the ambient temperature increasesand/or as the ambient humidity decreases. A second example of theboosted engine method optionally includes the first example and furtherincludes, wherein retaining the cooled compressed air includes closing athrottle coupled downstream of an intake compressor in the air intakepassage, and wherein the heat transferred is determined as a function ofan initial temperature of the cooled compressed air and a durationelapsed since the closing of the throttle. A third example of theboosted engine method optionally includes one or more of the first andsecond examples, and further includes, wherein the compressed air isreleased responsive to higher than threshold heat transfer while at thelower engine load. A fourth example of the boosted engine methodoptionally includes the first through third examples, and furtherincludes, responsive to lower than threshold heat transfer while at thelower engine load, releasing the compressed air responsive to anincrease in operator torque demand. A fifth example of the boostedengine method optionally includes the first through fourth examples, andfurther includes, wherein the air intake passage is coupled to the ductat a location upstream of an intake compressor. A sixth example of theboosted engine method optionally includes the first through fifthexamples, and further includes, wherein drawing cool compressed air atthe higher engine load includes increasing an opening of a boostthrottle coupled in the air intake passage to draw air via the intakecompressor, and through a charge air cooler located downstream of thecompressor, into the engine, and wherein retaining cooled compressed airin the air intake passage at the lower engine load includes not flowingair through the compressor and closing the boost throttle. A seventhexample of the boosted engine method optionally includes the firstthrough sixth examples, and further includes, decreasing the opening ofan air throttle coupled in the duct at the higher engine load, thedecreasing the opening of the air throttle based on the increasing theopening of the boost throttle. An eighth example of the boosted enginemethod optionally includes the first through seventh examples, andfurther includes, wherein releasing the compressed air includes:increasing the opening of the boost throttle while at the lower engineload; decreasing the opening of the air throttle based on the opening ofthe boost throttle; and retarding spark timing based on engine torquewith the increased opening of the boost throttle relative to operatortorque demand at the lower engine load. A ninth example of the boostedengine method optionally includes the first through eighth examples, andfurther includes, wherein coolant is circulated through the charge aircooler while drawing cool compressed air into the engine via the airintake passage, and wherein coolant is not circulated through the chargeair cooler while retaining the compressed air in the air intake passage.

As an embodiment, a method for a boosted engine includes: responsive toa tip-in, increasing a boost throttle opening to draw cool compressedair from downstream of a charge air cooler (CAC) into an engine via aboost passage; responsive to a tip-out, increasing an air throttleopening to draw ambient air from upstream of the CAC into the engine viaan air passage while retaining the compressed air in the boost passage;and opening the boost throttle following the tip-out based on heattransfer to the compressed air in the duct relative to operator torquedemand. In a first example of the boosted engine method, opening theboost throttle following the tip-out includes: opening the boostthrottle in response to heat transfer to the compressed air in the ductbeing higher than a threshold amount while operator torque demand isbelow a threshold demand; and opening the boost throttle in response toan increase in operator torque demand to higher than the thresholddemand while heat transfer to the compressed air in the duct is lowerthan the threshold amount. A second example of the boosted engine methodoptionally includes the first example and further includes, responsiveto opening the boost throttle while operator torque demand is below thethreshold demand, adjusting one or more engine operating parameters toreduce engine torque output, the adjusting including retarding sparktiming, adjusting fuel injection timing, adjusting valve timing, andadjusting a split ratio of fuel delivered via direct injection relativeto port injection. A third example of the boosted engine methodoptionally includes one or more of the first and second examples, andfurther includes, wherein the boost passage includes a pressure reliefvalve upstream of the compressor, the boost passage is coupled to theair passage upstream of the pressure relief valve, increasing the boostthrottle opening includes decreasing the air throttle opening, andincreasing the air throttle opening includes decreasing the boostthrottle opening. A fourth example of the boosted engine methodoptionally includes the first through third examples, and furtherincludes, estimating the heat transfer to the compressed air based oneach of ambient temperature and ambient humidity, the heat transferincreased as the ambient temperature increases and the ambient humiditydecreases. As an embodiment, a boosted engine system includes: anengine; a first air intake passage coupled to the engine via a firstthrottle; a second air intake passage housing a pressure relief valve, acompressor located downstream of the valve, and a charge air coolerlocated downstream of the compressor, the second air intake passagecoupled to the engine via a second throttle, the first air intakepassage coupled to the second air intake passage upstream of thepressure relief valve; an ambient temperature sensor and an ambienthumidity sensor coupled to the first air intake passage; an acceleratorpedal for receiving an operator torque demand; and a controller withcomputer-readable instructions stored on non-transitory memory for:adjusting an opening of the first throttle relative to the secondthrottle based on the operator torque demand; and while operating withthe second throttle fully closed, adjusting a timing of opening thesecond throttle based on a rate of rise in temperature of the compressedair trapped in the second air intake passage. In a first example of theboosted engine system, wherein the adjusting the opening of the firstthrottle relative to the second throttle includes: as the operatortorque demand exceeds a threshold demand, increasing the opening of thesecond throttle relative to the first throttle; and as the operatortorque demand falls below the threshold demand, increasing the openingof the first throttle relative to the second throttle, and trapping anamount of air in the second air intake passage. A second example of theboosted engine method optionally includes the first example and furtherincludes, wherein the controller includes further instructions for:estimating the rate of rise in temperature of the compressed air trappedin the second air intake passage based on each of measured ambienttemperature, measured ambient humidity, initial temperature of thecompressed air at a time of fully closing the second throttle, and aduration elapsed since the full closing of the second throttle, theamount of heat transferred increased as one or more of the ambienttemperature increases, the ambient humidity decreases, the initialtemperature increases, and the elapsed duration increases. A thirdexample of the boosted engine system optionally includes one or more ofthe first and second examples, and further includes, wherein adjustingthe timing of opening the second throttle includes: transiently openingthe second throttle to release the trapped compressed air when the rateof temperature rise of the trapped compressed air is higher than athreshold amount while the operator torque demand is below the thresholddemand; and opening the second throttle while spooling up the compressorwhen the rate of temperature rise of the trapped compressed air is lowerthan the threshold amount while the operator torque demand exceeds thethreshold demand. A fourth example of the boosted engine systemoptionally includes the first through third examples, and furtherincludes, wherein the controller includes further instructions for:retarding spark timing from MBT while transiently opening the secondthrottle; and maintaining spark timing at MBT while opening the secondthrottle and spooling up the compressor.

Note that the example control and estimation routines included hereincan be used with various engine and/or vehicle system configurations.The control methods and routines disclosed herein may be stored asexecutable instructions in non-transitory memory and may be carried outby the control system including the controller in combination with thevarious sensors, actuators, and other engine hardware. The specificroutines described herein may represent one or more of any number ofprocessing strategies such as event-driven, interrupt-driven,multi-tasking, multi-threading, and the like. As such, various actions,operations, and/or functions illustrated may be performed in thesequence illustrated, in parallel, or in some cases omitted. Likewise,the order of processing is not necessarily required to achieve thefeatures and advantages of the example embodiments described herein, butis provided for ease of illustration and description. One or more of theillustrated actions, operations and/or functions may be repeatedlyperformed depending on the particular strategy being used. Further, thedescribed actions, operations and/or functions may graphically representcode to be programmed into non-transitory memory of the computerreadable storage medium in the engine control system, where thedescribed actions are carried out by executing the instructions in asystem including the various engine hardware components in combinationwith the electronic controller.

It will be appreciated that the configurations and routines disclosedherein are exemplary in nature, and that these specific embodiments arenot to be considered in a limiting sense, because numerous variationsare possible. For example, the above technology can be applied to V-6,I-4, I-6, V-12, opposed 4, and other engine types. The subject matter ofthe present disclosure includes all novel and non-obvious combinationsand sub-combinations of the various systems and configurations, andother features, functions, and/or properties disclosed herein.

The following claims particularly point out certain combinations andsub-combinations regarded as novel and non-obvious. These claims mayrefer to “an” element or “a first” element or the equivalent thereof.Such claims should be understood to include incorporation of one or moresuch elements, neither requiring nor excluding two or more suchelements. Other combinations and sub-combinations of the disclosedfeatures, functions, elements, and/or properties may be claimed throughamendment of the present claims or through presentation of new claims inthis or a related application. Such claims, whether broader, narrower,equal, or different in scope to the original claims, also are regardedas included within the subject matter of the present disclosure.

The invention claimed is:
 1. A method for an engine, comprising:estimating operating conditions of the engine and determining that theengine is being operated at a first engine load via an electroniccontroller; responsive to determining that the engine is being operatedat the first engine load, where the first engine load is lower than asecond engine load, adjusting a valve via the electronic controller, andstoring cooled boost air in an intake passage while simultaneouslyflowing ambient air into an intake manifold of the engine for combustionvia a duct; and then determining an inferred temperature of the storedcooled boost air has exceeded a threshold temperature via the electroniccontroller; and responsive to determining the inferred temperature ofthe stored cooled boost air has exceeded the threshold temperature,adjusting the valve via the electronic controller, and decreasing anamount of the ambient air flowed into the intake manifold of the enginefor combustion and flowing the stored cooled boost air to the intakemanifold for combustion.
 2. The method of claim 1, wherein the valve isa boost throttle coupled to the intake passage is opened to flow thestored cooled boost air to the intake manifold.
 3. The method of claim2, wherein the boost throttle is further opened to flow the cooled boostair into the intake manifold responsive to a period of time that thecooled boost air has been stored in the intake passage exceeding a timethreshold.
 4. The method of claim 1, wherein decreasing the amount ofthe ambient air flowed into the intake manifold of the engine includesadjusting a position of an air throttle coupled in the duct to a moreclosed position.
 5. The method of claim 1, further comprising, at higherengine load, drawing further cooled boost air directly into the intakemanifold of the engine via the intake passage.